US4168948A - Burner assembly - Google Patents

Burner assembly Download PDF

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Publication number
US4168948A
US4168948A US05/785,311 US78531177A US4168948A US 4168948 A US4168948 A US 4168948A US 78531177 A US78531177 A US 78531177A US 4168948 A US4168948 A US 4168948A
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US
United States
Prior art keywords
fuel
inlet
air
burner assembly
combustion chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/785,311
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English (en)
Inventor
Toshimasa Okamoto
Shohachiro Shimpo
Ryoetsu Kikuchi
Fumio Ikeda
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TOMOE SHOKAI KK
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TOMOE SHOKAI KK
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Application filed by TOMOE SHOKAI KK filed Critical TOMOE SHOKAI KK
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/001—Spraying nozzle combined with forced draft fan in one unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply

Definitions

  • the present invention relates in general to a burner assembly or combustor assembly for a boiler or steam generator, and more particularly to a burner assembly capable of preventing progressive energy of a pneumatic oscillation plane progressive waves from adversely affecting an operation of a principal mechanism provided in the inside of a burner body and aiding in balancing distribution of the resultant energy, and still more particularly to a burner assembly for providing an efficient combustion system.
  • FIG. 1(a) which, though, shows the present invention.
  • fuel such as gas or oil
  • a combustion air is supplied in the direction of arrow "R” by driving a fan or blower 3 and gyratorily agitated by a diffuser 6 into air-fuel mixture particles, which are then issued into a furnace 11 through a fuel inlet 7 in the direction of arrow"S.”
  • the air-fuel mixture particles are ignited by a ignition rod 5
  • the air-fuel mixture particles form a flame, which is denoted by "X”
  • Y pneumatic oscillations
  • the pneumatic oscillations (Y) resonate by reflection at the inner walls of the furnace 11, thus extremely increasing the sound pressure within the furnace 11, that is, the amplitude of the pneumatic oscillations.
  • the pneumatic oscillations (Y) at complicated frequencies produced within the furnace 11 due to the sound of combusion proceeds in the form of pneumatic oscillation plane progressive waves, designated by "Z,” from the fuel inlet 7 through a fuel duct 1 and the burner body 1, that is, through diffuser 6, nozzle 4, ignition rod 5 and blower 3, in the direction opposite to the stream line of the air fuel mixture particles, which is shown by "S,” and in the direction opposite to the direction of supply of combustion air (R) and is propagated from an inlet 8 into atmosphere.
  • the air-fuel mixture particles issued into the front of the fuel inlet 7 are partly pushed back through a flame inlet 2 into the burner body 1 by the progressive energy of the pneumatic oscillation plane progressive waves (Z), to float and be attached to stain the rear surface of the diffuser 6 and inner surface of the ignition rod 5, nozzle 4 and ignition tube 2.
  • the form of injection of fuel from the nozzle 4 is disturbed, namely, the fuel injection is deformed, preventing a desirable ignition of the ignition rod 5 and presenting an outcome of various troubles.
  • the air-fuel mixture particles are partly ignited by the combustion flame (X) in front of the flame inlet 7, thus giving rise to the so-called "flashback."
  • the pneumatic oscillation plane progressive waves which are of complicated frequencies due to the combustion sound, are directly propagated from the air inlet 8 into the room where the burner is installed, thus giving rise to various drawbacks such as generation of a great noise and resonation of doors and windows of the room.
  • the conventional burner in order to prevent as much as possible pneumatic oscillations (Y) at complicated frequencies due to combustion sound from entering the burner body 1 and fuel duct 2 in the form of the pneumatic oscillation plane progressive waves (Z), the conventional burner has adopted a structure where an area of communication of the furnace 11 with respect to burner body 1 and fuel duct 2 is extremely reduced by building the fuel inlet 7 smaller or the diffuser 6 larger.
  • a blower of large size and capable of producing high pressure is required.
  • an object of the present invention is to basically preclude the various drawbacks inherent in the prior-art burner by means of a very simple mechanism.
  • Another object of the present invention is to provide a burner assembly which allows a continuation of normal combustion with a normal form of fuel injection from a nozzle.
  • Another object of the present invention is to provide a burner assembly which provides an efficient combustion system without so-called flashback.
  • Another object of the present invention is to provide a burner assembly which allows an efficient combusion by a smaller blower.
  • Further object of the present invention is to provide a burner assembly, which is compact, simple in structure and reliable in its operation.
  • Additional object of the present invention is to provide a burner assembly which prevents the generation of violent sound of combustion.
  • FIG. 1(a) and FIG. 1(b) are longitudinal sectional view and transversal plan view, respectively, of a burner assembly fixed to a combustion housing, in a first embodiment of the invention
  • FIG. 2 is a transversal plan view of a burner assembly according to a second embodiment of the invention.
  • FIG. 3 is a transversal plan view of a burner assembly according to a third embodiment of the invention.
  • FIG. 4 is a transversal plan view of a burner assembly according to a fourth embodiment of the invention.
  • FIG. 5 is a transversal plan view of a burner assembly according to a fifth embodiment of the invention.
  • FIGS. 6, 7 and 8 show data obtained through 1/3 octave band analysis of pneumatic oscillations due to combustion sound in case where an oscillatory combustion is eliminated with the burner assembly of the first embodiment shown in FIGS. 1(a) and 1(b);
  • FIG. 9 shows data about the attenuation of pneumatic oscillation in cases of FIGS. 6, 7 and 8;
  • FIG. 10 shows data obtained through experiments similar to those of FIGS. 6, 7 and 8, conducted with a vertical-type boiler.
  • a burner body 1 is fixed to a combustion housing 11 of a furnace at a fuel inlet 7 through a fuel duct 2.
  • the housing 11 has a gas outlet 10 at its upper portion.
  • Disposed within the burner body 1 and the fuel duct 2 are such principal mechanism of the burner as a fan 3, a fuel nozzle 4, an ignition rod 5 and an air-fuel mixture diffuser 6.
  • the air-fuel mixture diffuser 6 is disposed between the elements 4, 5 and the fuel inlet 7 but closely adjacent to the inlet 7.
  • the burner body has a casing 1a which has an inlet 1b opposite to the closed side 1c thereof.
  • a motor 8 which is mechanically connected with the fan.
  • An intake damper 9 is disposed within a sleeve 12 which is communicated with the opened side, namely, the inlet 1b of the casing. It is preferred that the casing 1a and sleeve 12 are of integral structure.
  • An air duct 13 made of a desired metal such as steel, or of a desired plastics is connected to the sleeve 12 with its other end 14 being opened.
  • a cylindrical member 17 is removably connected by set screws 15, 16 to the air duct 13.
  • the cylindrical member 17 is made of any desired materials, such as metal or plastics.
  • a bellows-like air duct 13' is connected to the sleeve 12 with its other end 14 being opened such that the air duct 13' may be telescoped.
  • a cylindrical member 17' which has a plurality of small apertures 18 is connected to an air-duct 13.
  • a sound-absorbing material 16 Around the apertured cylindrical member 17' is disposed a sound-absorbing material 16 so that the combination of the apertured member 17' with the sound-absorbing material 16 form a silencer device 19.
  • a silencer device 19 which is quite same as that of the embodiment of FIG. 4, is connected to a cylindrical member 17 which is removably connected to an air duct 13.
  • the construction of the air duct 13 and the cylindrical member 17 is same with that of FIG. 2.
  • a desired sound absorbing material may be disposed on the inner surface of the cylindrical or bellows-like air duct 13, 13' illustrated in FIGS. 1 through 5.
  • an outer cylindrical member 13' which surrounds the air duct 13.
  • the outer cylindrical member 13' is of an adjustable length and is secured by set screws 15 to the air duct 13. Therefore, the air duct 13 is telescoped by means of the outer cylindrical member 13' in function.
  • the air duct 13 is of bellows-like structure.
  • the length of the air duct 13 is made adjustable in accordance with main pneumatic oscillation frequencies including center frequency of pneumatic oscillations at complicated frequencies (Y) due to combustion sound within the housing 11 of the furnace, the combustion sound varying with various conditions such as fuel, furnace temperature and fun.
  • a combustion sound at frequencies other than the main pneumatic frequencies which include center frequency directly propagating from the open end 14 into the room where the burner is installed, is absorbed, so that it is possible to obtain extreme effects of prevention of a combustion sound.
  • the pneumatic oscillations are rendered into pneumatic oscillation plane progressive waves (Z), which proceed from the inlet 8 into the air duct 13 and are propagated into an atmosphere through the open end 14.
  • the burner assembly of the present invention comprises an air duct 13 which is provided at the inlet 8 of the fan 3 and constitutes an air duct mechanism or an air passage, of the desired length to cause resonation of waves of main oscillation frequencies which contain a center frequency among pneumatic oscillations (Y) at complicated frequencies due to combustion sound grown within the housing 11 of the furnace
  • plane progressive waves of main frequencies which contain a center frequency among pneumatic plane progressive waves (Z) proceeding in the direction opposite to the direction of supply of combustion air (R) are converted into pneumatic oscillation plane stationary waves (T) to extremely and desirably reduce progressive energy of the pneumatic oscillation plane progressive waves (Z) for preventing various adverse effects upon the operation of the burner mechanism of the burner body 1, thus completely precluding or eliminating the aforesaid drawbacks which are inherent in the conventional prior art burners such as flashback phenomenon, breathing combustion, the necessity for large size and high pressure fan and an increase of the burner size.
  • the pneumatic oscillation plane stationary wave (T) since the pneumatic oscillation plane stationary wave (T) resonates violently within the air duct 13 of the burner assembly, it is converted into heat energy due to friction caused by an active movement of the air particles and is hence gradually attenuated with the lapse of time.
  • T pneumatic oscillation plane stationary wave
  • FIGS. 6, 7 and 8 compare data obtained through 1/3 octave band analysis of pneumatic oscillations due to combustion sound in case where oscillatory combustion is actually caused by providing the prior-art burner (symbol a) and cases where the oscillatory combustion is eliminated by varying the length of the air duct 0.15 meter in inner diameter, which is provided in the burner of the first embodiment of the invention, to 0.8 meter (symbol b in FIG. 6), 1.6 meter (symbol b in FIG. 7) and 2.4 meter (symbol b in FIG. 8) respectively.
  • FIG. 9 shows data about the fact that the effects according to the invention are pronounced, with the difference between the levels of symbols a and b shown in FIGS. 6, 7 and 8, that is, the attenuation of the pneumatic oscillations with the burner of the first embodiment according to the invention, being represented by respective symbols c, d and e.
  • the afore-mentioned data indicates that the most pronounced effects according to the invention can be obtained in case where the air duct constituting the mechanism feature of the invention has a length of 1.6 meter.
  • FIG. 10 shows data obtained by similar experiments conducted with a vertical boiler. The most pronounced effect is obtained in case where the air duct has a length of 2.7 meters.
  • symbol a indicates the case where the conventional burner is provided
  • symbol b shows where the burner of the first embodiment of the invention is provided.
  • the center frequency of the pneumatic oscillation due to the combustion sound varies with various conditions such as a burner fuel inlet, shape and dimensions of the furnace, combustion temperature and external ambient temperature, it may usually be thought to be within a range of 20 to 200 Hz.
  • the length of the air duct according to the invention may range from 0.4 to 4.0 meters in practice since pronounced effects can be expected, although they may vary to some extents, even if the length corresponding to the center frequency of the pneumatic oscillation due to the combustion sound is slightly deviated. Further, regarding the sectional profile, extremely superior effects can be obtained with circuler or regular polygon form compared to the elliptical or rectangular form.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Air Supply (AREA)
US05/785,311 1976-04-08 1977-04-06 Burner assembly Expired - Lifetime US4168948A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP51-39664 1976-04-08
JP3966476A JPS52122934A (en) 1976-04-08 1976-04-08 Burner

Publications (1)

Publication Number Publication Date
US4168948A true US4168948A (en) 1979-09-25

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ID=12559343

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/785,311 Expired - Lifetime US4168948A (en) 1976-04-08 1977-04-06 Burner assembly

Country Status (7)

Country Link
US (1) US4168948A (enrdf_load_stackoverflow)
JP (1) JPS52122934A (enrdf_load_stackoverflow)
CA (1) CA1054046A (enrdf_load_stackoverflow)
CH (1) CH625870A5 (enrdf_load_stackoverflow)
DE (1) DE2712326C2 (enrdf_load_stackoverflow)
FR (1) FR2347613A1 (enrdf_load_stackoverflow)
GB (1) GB1552553A (enrdf_load_stackoverflow)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4230449A (en) * 1979-03-19 1980-10-28 Coen Company Self contained compact burner
US4476850A (en) * 1982-09-02 1984-10-16 Carrier Corporation Noise reducing heat exchanger assembly for a combustion system
US4568264A (en) * 1983-01-14 1986-02-04 Lennox Industries, Inc. Combustion chamber construction
US4699588A (en) * 1986-03-06 1987-10-13 Sonotech, Inc. Method and apparatus for conducting a process in a pulsating environment
US4770626A (en) * 1986-03-06 1988-09-13 Sonotech, Inc. Tunable pulse combustor
US5408986A (en) * 1993-10-21 1995-04-25 Inter-City Products Corporation (Usa) Acoustics energy dissipator for furnace
US5816793A (en) * 1994-06-01 1998-10-06 Matsushita Electric Industrial Co., Ltd. Combustion apparatus
RU2242676C2 (ru) * 2002-02-01 2004-12-20 ОАО Научно-производственное предприятие "ЭГА" Горелочное устройство направленного нагрева
US20060014114A1 (en) * 2004-07-15 2006-01-19 Alexander Groehl Gas-fired heating apparatus
US20100068668A1 (en) * 2008-09-16 2010-03-18 Siemens Building Technologies Hvac Products Gmbh Gas burner
US20130164697A1 (en) * 2011-12-27 2013-06-27 Rinnai Corporation Combustion Apparatus
US20220120469A1 (en) * 2020-10-19 2022-04-21 Volvo Truck Corporation Acoustic resonator for fan
EP4375573A1 (en) * 2022-11-23 2024-05-29 Ademco Inc. A silencer

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2918416C2 (de) * 1979-05-08 1985-05-15 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Vergasungsölbrenner
JPS5852419U (ja) * 1981-10-07 1983-04-09 東京ガス・エンジニアリング株式会社 骨材等の乾燥機
DE3347204C2 (de) * 1983-12-27 1990-08-02 Max Weishaupt Gmbh, 7959 Schwendi Luftansauggehäuse für einen Gebläsebrenner
GB2219389B (en) * 1988-06-03 1992-04-15 William Henry Deryk Morris Improved pressure jet burner
US5083914A (en) * 1989-08-22 1992-01-28 Morris William H D Adjustable pressure jet burner
GB2241286A (en) * 1990-02-23 1991-08-28 Heating World Central heating boiler exhaust silencing
IT1306039B1 (it) * 1998-02-27 2001-05-29 Walkover S R L Generatore d'aria calda per riscaldamento ambientale alimentato a gas
CN113124424B (zh) * 2019-12-31 2022-06-17 中国航发商用航空发动机有限责任公司 一种双层壁火焰筒及其电嘴安装座

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2046193A (en) * 1931-01-03 1936-06-30 Burgess Lab Inc C F Muffler
US2150782A (en) * 1937-04-27 1939-03-14 Micro Westco Inc Attachment for liquid fuel burners
US2670034A (en) * 1951-08-02 1954-02-23 Harry E Thompson Air compensator for gas burners
DE1009429B (de) * 1955-06-18 1957-05-29 Daimler Benz Ag Ansaugleitung fuer Brennkraftmaschinen
US2942683A (en) * 1953-06-01 1960-06-28 Phillips Petroleum Co Gas intake silencer
US2955671A (en) * 1954-08-25 1960-10-11 Leistritz Hans Karl Induction silencers for internal combustion engine carburetors
GB891757A (en) * 1961-01-05 1962-03-21 Morris Motors Ltd Combined air cleaner and silencer units
US3712416A (en) * 1971-11-26 1973-01-23 Donaldson Co Inc Air intake silencer
US3940234A (en) * 1974-05-28 1976-02-24 John Zink Company Noiseless pms burner

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1551757B2 (de) * 1967-03-31 1977-01-20 Böhler-Zenkner GmbH & Co KG Strömungstechnik, 4005 Meerbusch Brenner fuer fluessigen brennstoff mit einem querstromgeblaese
JPS4940838B1 (enrdf_load_stackoverflow) * 1970-03-05 1974-11-05
JPS485064U (enrdf_load_stackoverflow) * 1971-05-27 1973-01-20
AT321748B (de) * 1971-11-02 1975-04-10 Webasto Werk Baier Kg W Mit flüssigem Brennstoff betriebene Heizvorrichtung
JPS5026441B2 (enrdf_load_stackoverflow) * 1971-12-21 1975-09-01
GB1367974A (en) * 1972-05-31 1974-09-25 Texaco Development Corp Oil burner

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2046193A (en) * 1931-01-03 1936-06-30 Burgess Lab Inc C F Muffler
US2150782A (en) * 1937-04-27 1939-03-14 Micro Westco Inc Attachment for liquid fuel burners
US2670034A (en) * 1951-08-02 1954-02-23 Harry E Thompson Air compensator for gas burners
US2942683A (en) * 1953-06-01 1960-06-28 Phillips Petroleum Co Gas intake silencer
US2955671A (en) * 1954-08-25 1960-10-11 Leistritz Hans Karl Induction silencers for internal combustion engine carburetors
DE1009429B (de) * 1955-06-18 1957-05-29 Daimler Benz Ag Ansaugleitung fuer Brennkraftmaschinen
GB891757A (en) * 1961-01-05 1962-03-21 Morris Motors Ltd Combined air cleaner and silencer units
US3712416A (en) * 1971-11-26 1973-01-23 Donaldson Co Inc Air intake silencer
US3940234A (en) * 1974-05-28 1976-02-24 John Zink Company Noiseless pms burner

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4230449A (en) * 1979-03-19 1980-10-28 Coen Company Self contained compact burner
US4476850A (en) * 1982-09-02 1984-10-16 Carrier Corporation Noise reducing heat exchanger assembly for a combustion system
US4568264A (en) * 1983-01-14 1986-02-04 Lennox Industries, Inc. Combustion chamber construction
US4699588A (en) * 1986-03-06 1987-10-13 Sonotech, Inc. Method and apparatus for conducting a process in a pulsating environment
US4770626A (en) * 1986-03-06 1988-09-13 Sonotech, Inc. Tunable pulse combustor
US5408986A (en) * 1993-10-21 1995-04-25 Inter-City Products Corporation (Usa) Acoustics energy dissipator for furnace
US5816793A (en) * 1994-06-01 1998-10-06 Matsushita Electric Industrial Co., Ltd. Combustion apparatus
RU2242676C2 (ru) * 2002-02-01 2004-12-20 ОАО Научно-производственное предприятие "ЭГА" Горелочное устройство направленного нагрева
US20060014114A1 (en) * 2004-07-15 2006-01-19 Alexander Groehl Gas-fired heating apparatus
US7341448B2 (en) * 2004-07-15 2008-03-11 Ceramat, S.Coop. Gas-fired heating apparatus
US20100068668A1 (en) * 2008-09-16 2010-03-18 Siemens Building Technologies Hvac Products Gmbh Gas burner
US20130164697A1 (en) * 2011-12-27 2013-06-27 Rinnai Corporation Combustion Apparatus
US9127839B2 (en) * 2011-12-27 2015-09-08 Rinnai Corporation Combustion apparatus
US20220120469A1 (en) * 2020-10-19 2022-04-21 Volvo Truck Corporation Acoustic resonator for fan
US11815285B2 (en) * 2020-10-19 2023-11-14 Volvo Truck Corporation Acoustic resonator for fan
EP4375573A1 (en) * 2022-11-23 2024-05-29 Ademco Inc. A silencer

Also Published As

Publication number Publication date
JPS52122934A (en) 1977-10-15
DE2712326A1 (de) 1977-10-20
GB1552553A (en) 1979-09-12
CH625870A5 (enrdf_load_stackoverflow) 1981-10-15
CA1054046A (en) 1979-05-08
DE2712326C2 (de) 1984-04-26
FR2347613B1 (enrdf_load_stackoverflow) 1980-10-03
FR2347613A1 (fr) 1977-11-04

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